JP4282415B2 - Pressure regulating valve - Google Patents

Pressure regulating valve Download PDF

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JP4282415B2
JP4282415B2 JP2003320247A JP2003320247A JP4282415B2 JP 4282415 B2 JP4282415 B2 JP 4282415B2 JP 2003320247 A JP2003320247 A JP 2003320247A JP 2003320247 A JP2003320247 A JP 2003320247A JP 4282415 B2 JP4282415 B2 JP 4282415B2
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pressure
valve
spring
fluid
setting
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進 中川
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フシマン株式会社
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Description

本発明は、電気や空気圧などの動力を必要とせず、高低２種類の設定圧力を必要とされる圧力調整を１台の圧力調整弁のみで行うことを可能にするものであって、流体を流し始めてから絞り弁の開度によって設定される所望の時間経過後に自動的かつ純機械的に設定圧力を低圧から高圧に切り替えることができる圧力調整弁に関する。   The present invention does not require power such as electricity or air pressure, and makes it possible to perform pressure adjustment that requires two kinds of high and low set pressures with only one pressure regulating valve. The present invention relates to a pressure regulating valve capable of automatically and purely mechanically switching a set pressure from a low pressure to a high pressure after a desired time set by the opening of a throttle valve has elapsed since the beginning of flow.

ダイアフラム、ピストン等の圧力検出手段の片側に制御対象となる流体圧を加え、反対側に圧力設定用の調節ばねのばね荷重を付加することにより前記流体圧を一定に調節する圧力調整弁は、従来から種々提案されている（例えば、特許文献１〜３参照）。   A pressure adjustment valve that adjusts the fluid pressure to a constant value by adding a fluid pressure to be controlled to one side of a pressure detection means such as a diaphragm or a piston and adding a spring load of an adjustment spring for pressure setting to the opposite side. Various proposals have been made conventionally (see, for example, Patent Documents 1 to 3).

特開平０９−２２９２１８号公報JP 09-229218 A 特開２００３−１４８２６３号公報JP 2003-148263 A 特開平０９−１３８７０９号公報JP 09-138709 A

このような圧力調整弁において、圧力設定用の調節ねじを回転することにより１種類の圧力設定が可能である。また、例えばこのような圧力調整弁をパイロット作動式減圧弁として用い主弁の二次側配管が極端に長い場合、圧力調整弁を高い設定圧力で流体を全閉状態から一気に流すと、ウオーターハンマー現象（水激現象）によって主弁の二次側配管が破損するおそれがあるようなときは、高低２種類の圧力設定が可能な調整弁が要求される。このような要求に対しては、従来は２台の圧力調整弁を電磁弁や空気式の切換弁で切替えることにより実現していた。また、切換えの時間間隔設定が必要な場合は、電気式のタイマーを用いていた。   In such a pressure regulating valve, one type of pressure can be set by rotating an adjusting screw for pressure setting. Also, for example, when such a pressure regulating valve is used as a pilot-actuated pressure reducing valve and the secondary side piping of the main valve is extremely long, if the pressure regulating valve is made to flow at once from a fully closed state with a high set pressure, a water hammer When there is a possibility that the secondary side piping of the main valve may be damaged due to a phenomenon (aquatic phenomenon), an adjustment valve capable of setting two types of pressures is required. Conventionally, such a requirement has been realized by switching two pressure regulating valves with a solenoid valve or a pneumatic switching valve. In addition, when it is necessary to set the switching time interval, an electric timer is used.

しかしながら、電磁弁や空気式切換弁で設定圧力の切替えを行うようにした圧力調整弁は、設置場所の環境によっては電気や空気圧などの動力を得ることが困難であったり、あるいは停電や空気源の故障などにより動力が得られなくなった場合には全く使用することができなくなるという問題があった。
また、電気や空気圧などの動力を用いずに純機械的に圧力調整を行うようにした圧力調整弁も考えられるが、そのような従来技術について、出願人は出願時までに関連する先行技術文献を発見することができなかった。よって、本発明に密接に関連する先行技術文献情報を開示していない。 However, the pressure adjustment valve that switches the set pressure with a solenoid valve or pneumatic switching valve may be difficult to obtain power such as electricity or air pressure depending on the installation site environment, There is a problem that it cannot be used at all when power cannot be obtained due to a failure of the device.
In addition, a pressure regulating valve that performs pressure regulation purely mechanically without using power such as electricity or air pressure is also conceivable. With regard to such conventional technology, the applicant has obtained prior art documents related to the time of filing. Could not be found. Therefore, prior art document information closely related to the present invention is not disclosed.

本発明は上記した従来の問題を解決するためになされたもので、その目的とするところは、電気や空気圧などの動力を必要とせず、使用する流体の流体圧自体を利用することにより設定圧力を純機械的に切り替えることができるようにした圧力調整弁を提供することにある。   The present invention has been made in order to solve the above-described conventional problems. The object of the present invention is not to require power such as electricity or air pressure, but by using the fluid pressure itself of the fluid to be used. It is an object of the present invention to provide a pressure regulating valve that can be switched mechanically.

上記目的を達成するために第１の発明は、圧力検出手段の片側に制御対象の流体圧を加え、反対側に圧力設定用の調節ばねのばね荷重を付加することにより前記流体圧を一定に調節する圧力調整弁において、前記圧力検出手段に前記調節ばねのばね荷重を付加する低圧設定手段と、前記低圧設定手段を押し下げることにより前記調節ばねのばね荷重を増大させ前記流体圧を低圧から高圧に設定する高圧設定手段と、前記高圧設定手段の一部が挿入されたシリンダと、前記シリンダ内を前記高圧設定手段が挿入される大気圧室と圧力室とに仕切り、高圧設定時に前記高圧設定手段を押し下げるピストンと、前記ピストンに前記圧力室方向の復帰習性を付与する復帰用ばねと、弁本体への流体供給開始と同時に前記圧力室に高圧設定用の圧力を導く導管と、前記導管の途中に接続された可変型絞り弁とを備えたものである。   In order to achieve the above object, according to a first aspect of the present invention, the fluid pressure to be controlled is applied to one side of the pressure detecting means, and the fluid pressure is made constant by adding a spring load of an adjustment spring for pressure setting to the opposite side. In the pressure adjusting valve to be adjusted, low pressure setting means for adding a spring load of the adjusting spring to the pressure detecting means, and the spring load of the adjusting spring is increased by depressing the low pressure setting means so that the fluid pressure is increased from low pressure to high pressure. A high pressure setting means for setting the pressure, a cylinder in which a part of the high pressure setting means is inserted, an atmospheric pressure chamber in which the high pressure setting means is inserted and a pressure chamber are partitioned, and the high pressure setting is performed at the time of high pressure setting. A piston that pushes down the means, a return spring that imparts a return habit to the piston in the direction of the pressure chamber, and a pressure for setting a high pressure to the pressure chamber at the same time as the fluid supply to the valve body starts. A conduit, in which a variable throttle valve connected in the middle of the conduit.

第２の発明は、上記第１の発明において、前記シリンダを前記低圧設定手段に対して高さ調整可能に取付けたものである。   According to a second invention, in the first invention, the cylinder is attached to the low pressure setting means so as to be adjustable in height.

本発明は上記構成を採っているので、１台の圧力調整弁で高低２種類の圧力設定を可能とし、かつ流体を弁本体に流し始めてから可変型絞り弁の開度によって設定された必要とされる時間経過後に自動的かつ純機械的に設定圧力を低圧設定から高圧設定に切り替えることができる。可変型絞り弁の開度を変えると、時間を調節することができる。   Since the present invention adopts the above-described configuration, it is possible to set two kinds of pressure levels, one pressure adjusting valve, and the need to be set by the opening of the variable throttle valve after the fluid starts to flow through the valve body. The set pressure can be automatically and purely mechanically switched from the low pressure setting to the high pressure setting after the elapse of time. The time can be adjusted by changing the opening of the variable throttle valve.

以下、本発明を図面に示す実施例に基づいて詳細に説明する。
図１は本発明を高低２種類の圧力設定を可能にした圧力調整弁に適用した一実施の形態を示す断面図で、低圧設定時の状態を示す図である。図２は同圧力調整弁を配管に接続した状態を示す断面図で、シリンダーの圧力室に圧力調整弁の二次側圧力を可変型絞り弁を介して導入するようにした接続例を示す図である。図３は同圧力調整弁を高圧設定に切り替えた状態を示す断面図である。 Hereinafter, the present invention will be described in detail based on embodiments shown in the drawings.
FIG. 1 is a cross-sectional view showing an embodiment in which the present invention is applied to a pressure regulating valve capable of setting two kinds of high and low pressures, and shows a state at the time of low pressure setting. FIG. 2 is a cross-sectional view showing a state where the same pressure regulating valve is connected to the piping, and a diagram showing a connection example in which the secondary pressure of the pressure regulating valve is introduced into the cylinder pressure chamber via the variable throttle valve. It is. FIG. 3 is a cross-sectional view showing a state in which the pressure regulating valve is switched to a high pressure setting.

これらの図において、全体を符号１で示す圧力調整弁は、配管２（２Ａ，２Ｂ）の途中に接続された弁本体３と、この弁本体３内に上下動自在に挿入された弁体４とを備えている。弁本体３は、内部に隔壁５によって仕切られ左右両側に開放する流体流路６を有し、この流体流路６の入口部６ａに上流側配管２Ａが接続され、出口部６ｂに下流側配管２Ｂが接続されている。   In these drawings, a pressure regulating valve generally indicated by reference numeral 1 includes a valve body 3 connected in the middle of a pipe 2 (2A, 2B), and a valve body 4 inserted into the valve body 3 so as to be movable up and down. And. The valve body 3 has a fluid flow path 6 that is partitioned by a partition wall 5 and is open on both the left and right sides. An upstream pipe 2A is connected to an inlet 6a of the fluid flow path 6, and a downstream pipe is connected to an outlet 6b. 2B is connected.

また、弁本体３の上面には、弁本体３内の二次側圧力を検出する圧力検出手段７が取付けられている。圧力検出手段７はダイアフラムからなり、弁本体３の上面中央に形成した凹陥部８を覆うように取付けられ、外周縁部が上蓋９によって前記弁本体３の上面に密接され固定されている。ダイアフラム７と前記凹陥部８とによって囲まれた密閉空間はダイアフラム室１０を形成し、このダイアフラム室１０には前記弁本体２の上壁１２に形成して連通孔１３によって弁本体３内の二次側圧力が導かれる。   A pressure detection means 7 for detecting the secondary pressure in the valve body 3 is attached to the upper surface of the valve body 3. The pressure detecting means 7 is made of a diaphragm, is attached so as to cover a recessed portion 8 formed at the center of the upper surface of the valve body 3, and an outer peripheral edge portion is in close contact with and fixed to the upper surface of the valve body 3 by an upper lid 9. A sealed space surrounded by the diaphragm 7 and the recessed portion 8 forms a diaphragm chamber 10. The diaphragm chamber 10 is formed in the upper wall 12 of the valve body 2 and is formed in the valve body 3 by the communication hole 13. Secondary pressure is introduced.

前記弁本体３の下側中央には、前記弁体４を組み込むための開口部１４が形成されており、この開口部１４は栓体１５をＯリング１６を介して螺合することによって閉塞されている。   An opening 14 for assembling the valve body 4 is formed at the lower center of the valve body 3, and the opening 14 is closed by screwing the plug body 15 through an O-ring 16. ing.

前記弁体４は、前記隔壁５の中央に設けた流通孔１７を上下動自在に貫通するステム４Ａと、このステム４Ａの下端に一体に設けられ前記流通孔１７を隔壁５の下方から開閉する弁プラグ４Ｂと、前記ステム４Ａの上端に螺合するねじ４Ｃとで構成されている。流通孔１７の下端側開口部には、前記弁プラグ４Ｂの着座部を構成する筒部１８が一体に突設されている。前記ステム４Ａの上端部は、前記上壁１２に設けたステム用孔２０を摺動自在に貫通し、前記ダイアフラム７の中央部に固定されている。   The valve body 4 is integrally provided at the lower end of the stem 4 </ b> A that vertically penetrates the flow hole 17 provided in the center of the partition wall 5, and opens and closes the flow hole 17 from below the partition wall 5. It consists of a valve plug 4B and a screw 4C screwed into the upper end of the stem 4A. A cylindrical portion 18 constituting a seating portion of the valve plug 4B is integrally protruded from the lower end side opening of the flow hole 17. An upper end portion of the stem 4 </ b> A passes through a stem hole 20 provided in the upper wall 12 slidably and is fixed to the center portion of the diaphragm 7.

前記上蓋９の内部には、前記ダイアフラム７に前記弁本体３内の二次側圧力に対抗してばね荷重を付加する圧力設定用の調節ばね２２が組み込まれている。調節ばね２２は圧縮コイルばねからなり、上下一対のばね受け２３，２４間に弾装されている。上方側のばね受け２３は、押し棒２５の下端に固定されている。下方側のばね受け２４は、前記ステム４Ａの上端部に螺合するねじ４Ｃに螺合されており、前記ダイアフラム７の中央部を前記ステム４Ａの上端に設けたフランジ部２６に締め付けてシールしている。   An adjustment spring 22 for setting a pressure for applying a spring load to the diaphragm 7 against the secondary pressure in the valve body 3 is incorporated in the upper lid 9. The adjustment spring 22 is a compression coil spring and is elastically mounted between a pair of upper and lower spring receivers 23 and 24. The upper spring receiver 23 is fixed to the lower end of the push rod 25. The lower spring receiver 24 is screwed into a screw 4C that is screwed into the upper end portion of the stem 4A, and the center portion of the diaphragm 7 is fastened and sealed to a flange portion 26 provided at the upper end of the stem 4A. ing.

前記押し棒２５は、前記上蓋９に螺合するねじ体２８を上下動自在に貫通して上端部がシリンダ３０内に臨み、高圧設定時に前記ばね受け２３を下降させることにより前記調節ばね２２のばね荷重を増大させる高圧設定手段を構成している。   The push rod 25 passes through a screw body 28 screwed into the upper lid 9 so as to move up and down, the upper end faces the cylinder 30, and the spring receiver 23 is lowered when a high pressure is set, thereby lowering the adjustment spring 22. High pressure setting means for increasing the spring load is configured.

前記ねじ体２８は、前記ばね受け２３とともに低圧設定手段を構成するもので、下端部に前記上蓋９のねじ穴３１に螺合する雄ねじ部３２が形成され、上端部には前記シリンダ３０のねじ穴３３に螺合する雄ねじ部３４が形成され、軸心方向中央には回転操作部３５が一体に設けられている。回転操作部３５は、四角形または六角形の鍔状に形成され、スパナ等の適宜な工具によって回転操作される。また、前記雄ねじ部３２，３４には、設定圧力調整後の遊動を防止するためのロックナット３６，３７がそれぞれ螺合されている。   The screw body 28 constitutes a low pressure setting means together with the spring receiver 23, and a male screw portion 32 that is screwed into the screw hole 31 of the upper lid 9 is formed at the lower end portion, and the screw of the cylinder 30 is formed at the upper end portion. A male threaded portion 34 that is screwed into the hole 33 is formed, and a rotation operating portion 35 is integrally provided at the center in the axial center direction. The rotation operation unit 35 is formed in a square or hexagonal bowl shape, and is rotated by an appropriate tool such as a spanner. The male screw portions 32 and 34 are screwed with lock nuts 36 and 37 for preventing looseness after adjusting the set pressure, respectively.

前記シリンダ３０は、上端開口部に蓋体４０がＯリング４１を介して螺合され、内部がビストン４２によって２つの室４３，４４に仕切られている。上方側の室４３は前記下流側配管２Ｂに導管４５を介して接続されることにより、配管２内を流れる流体４６の二次側圧力が導かれる圧力室を形成している。前記導管４５は、一端が前記蓋体４０に設けた接続口４７に接続され、途中に流量可変型の絞り弁４８が接続されている。一方、下方側の室４４は、シリンダ３０の底部に設けた通気孔４９を介して外部に開放することにより大気圧室を形成している。   In the cylinder 30, a lid 40 is screwed into an upper end opening through an O-ring 41, and the inside is partitioned into two chambers 43 and 44 by a biston 42. The upper chamber 43 is connected to the downstream pipe 2B via a conduit 45, thereby forming a pressure chamber to which the secondary pressure of the fluid 46 flowing in the pipe 2 is guided. One end of the conduit 45 is connected to a connection port 47 provided in the lid body 40, and a variable flow rate type throttle valve 48 is connected in the middle. On the other hand, the lower chamber 44 is opened to the outside through a vent hole 49 provided at the bottom of the cylinder 30 to form an atmospheric pressure chamber.

さらに、前記大気圧室４４には、前記ピストン４２に圧力室４３方向の復帰習性を付与する復帰用ばね５０が弾装されている。復帰用ばね５０としては、比較的ばね力の弱い圧縮コイルばねが用いられる。シリンダ３０の内周面下部には、ピストン４２の下方への移動を制限する段部状のストッパ５１が設けられている。ピストン４２の下面中央には、設定圧力を低圧設定から高圧設定に切り替えるときに前記押し棒２５を押し下げる押圧部５２が一体に突設されている。このため、高圧設定手段は、押し棒２５だけでなく押し棒２５とピストン４２とで構成されているともいえる。   Further, the atmospheric pressure chamber 44 is provided with a return spring 50 that imparts a return behavior in the direction of the pressure chamber 43 to the piston 42. As the return spring 50, a compression coil spring having a relatively weak spring force is used. A stepped stopper 51 that restricts the downward movement of the piston 42 is provided at the lower part of the inner peripheral surface of the cylinder 30. At the center of the lower surface of the piston 42, a pressing portion 52 that pushes down the push rod 25 when the set pressure is switched from the low pressure setting to the high pressure setting is integrally projected. For this reason, it can be said that the high pressure setting means includes not only the push rod 25 but also the push rod 25 and the piston 42.

次に、上記構造からなる圧力調整弁１の動作について説明する。
図１に示すように圧力調整弁１を僅かに開弁させている状態で流体４６を配管２に流すと、この流体４６は上流側配管２Ａを通って弁本体３の入口部６ａから流体流路６内に流入し、流通孔１７を通り出口部６ｂから下流側配管２Ｂに流れる。このとき、流体流路６内を流れる流体４６の一部は、連通孔１３を経てダイアフラム室８内に入り、ダイアフラム室８内の圧力を上昇させる。このため、ダイアフラム７はダイアフラム室８内の圧力と調節ばね２２のばね荷重とが釣り合い状態を保つ位置まで上方に弾性変形し、弁体４を上昇させる。弁体４が上昇すると、弁プラグ４Ｂと流通孔１７との間隔は狭くなるため下流側配管２Ｂに流れる流体４６の流量が減少し、これによって下流側配管２Ｂ内の流体圧力が所定の圧力（低圧）に設定される。 Next, the operation of the pressure regulating valve 1 having the above structure will be described.
As shown in FIG. 1, when the fluid 46 is caused to flow through the pipe 2 while the pressure regulating valve 1 is slightly opened, the fluid 46 flows from the inlet 6a of the valve body 3 through the upstream pipe 2A. It flows into the channel 6, passes through the circulation hole 17, and flows from the outlet portion 6 b to the downstream pipe 2 </ b> B. At this time, a part of the fluid 46 flowing in the fluid flow path 6 enters the diaphragm chamber 8 through the communication hole 13 and increases the pressure in the diaphragm chamber 8. For this reason, the diaphragm 7 is elastically deformed upward to a position where the pressure in the diaphragm chamber 8 and the spring load of the adjustment spring 22 are kept in balance, and the valve body 4 is raised. When the valve body 4 is lifted, the distance between the valve plug 4B and the flow hole 17 is reduced, so that the flow rate of the fluid 46 flowing through the downstream pipe 2B is reduced. As a result, the fluid pressure in the downstream pipe 2B becomes a predetermined pressure ( Low pressure).

また、下流側配管２Ｂでの負荷流量が増加した場合は、ダイアフラム室８内の圧力が低下するからダイアフラム７を流体圧力が押し上げる力よりも調節ばね２２のばね荷重が大きくなって弁体４を下降させ、弁プラグ４Ｂと流通孔１７との間隔を広げて流量を増加させて下流側配管２Ｂの圧力低下を修正する。このように流体圧力は所定の圧力に調整される。   Further, when the load flow rate in the downstream side pipe 2B increases, the pressure in the diaphragm chamber 8 decreases, so the spring load of the adjustment spring 22 becomes larger than the force by which the fluid pressure pushes up the diaphragm 7, and the valve body 4 is The pressure drop of the downstream side pipe 2B is corrected by increasing the flow rate by lowering the distance between the valve plug 4B and the flow hole 17 and increasing the flow rate. Thus, the fluid pressure is adjusted to a predetermined pressure.

この二次側の設定圧力は、低圧設定手段を構成するばね受け２３をねじ体２８によって上下動させることにより可変することができる。すなわち、ロックナット３６，３７を緩めた後ねじ体２８をスパナ等によって回転させて上昇させると、調節ばね２２が伸張して上方側のばね受け２３を押し上げる。このため、調節ばね２２のダイアフラム７に対するばね荷重が減少して弁体４を上昇させる。この結果、弁プラグ４Ｂと流通孔１７との間隔が狭くなるため下流側配管２Ｂに流れる流体４６の流量が減少する。したがって、二次側流体圧は低くなる。反対に、ねじ体２８を下降させると、上方側のばね受け２３が調節ばね２２を押圧して圧縮させるため、調節ばね２２のダイアフラム７に対するばね荷重がさらに増大して弁体４を下降させる。この結果、弁プラグ４Ｂと流通孔１７との間隔がさらに拡大するため下流側配管２Ｂに流れる流体４６の流量が増加し、二次側流体圧を高くする。   The set pressure on the secondary side can be varied by moving the spring receiver 23 constituting the low pressure setting means up and down by the screw body 28. That is, after the lock nuts 36 and 37 are loosened, when the screw body 28 is rotated and lifted by a spanner or the like, the adjustment spring 22 extends to push up the upper spring receiver 23. For this reason, the spring load with respect to the diaphragm 7 of the adjustment spring 22 reduces, and the valve body 4 is raised. As a result, the interval between the valve plug 4B and the flow hole 17 is narrowed, so the flow rate of the fluid 46 flowing through the downstream pipe 2B is reduced. Therefore, the secondary fluid pressure is low. On the contrary, when the screw body 28 is lowered, the upper spring receiver 23 presses and compresses the adjustment spring 22, so that the spring load on the diaphragm 7 of the adjustment spring 22 further increases and the valve body 4 is lowered. As a result, the distance between the valve plug 4B and the flow hole 17 is further increased, so that the flow rate of the fluid 46 flowing through the downstream side pipe 2B is increased and the secondary side fluid pressure is increased.

前記下流側配管２Ｂとシリンダ３０の圧力室４３とは導管４５によって接続されているため、下流側配管２Ｂ内を流れる流体４６の一部は導管４５および絞り弁４８を通って圧力室４３に導かれる。このため、圧力室４３内の圧力が徐々に高くなり、ピストン４２を復帰用ばね５０に抗して押し下げる。そして、ピストン４２が図３に示すように所定量下降して押圧部５２により押し棒２５を押し下げると、上側方のばね受け２３が調節ばね２２を押圧して圧縮させるため、ダイアフラム８に対する調節ばね２２のばね荷重が増大し、ダイアフラム７を下方に押し下げる。このため、弁体４もダイアフラム７とともに下降して弁プラグ４Ｂと流通孔１７との間隔が拡大し、下流側配管２Ｂに流れる流体４６の流量を増加させる。この結果、流体４６の二次側流体圧は低圧から高圧に自動的に切り替えられる。   Since the downstream pipe 2B and the pressure chamber 43 of the cylinder 30 are connected by a conduit 45, a part of the fluid 46 flowing in the downstream pipe 2B is guided to the pressure chamber 43 through the conduit 45 and the throttle valve 48. It is burned. For this reason, the pressure in the pressure chamber 43 gradually increases and pushes down the piston 42 against the return spring 50. When the piston 42 is lowered by a predetermined amount as shown in FIG. 3 and the push bar 25 is pushed down by the pressing portion 52, the upper spring receiver 23 presses and compresses the adjustment spring 22, so that the adjustment spring for the diaphragm 8 is compressed. The spring load of 22 increases, and the diaphragm 7 is pushed downward. For this reason, the valve body 4 is also lowered together with the diaphragm 7, and the interval between the valve plug 4B and the flow hole 17 is enlarged, and the flow rate of the fluid 46 flowing through the downstream pipe 2B is increased. As a result, the secondary fluid pressure of the fluid 46 is automatically switched from a low pressure to a high pressure.

低圧設定状態から高圧設定状態に切り替えるために要する時間は、絞り弁４８の開度によって自由に可変設定することが可能である。すなわち、ピストン４２の移動速度は、絞り弁４８の開度、すなわち絞り弁４８を通る流体の時間当たりの流量によって決定されるため、絞り弁４８の開度を大きくすると、ピストン４２の移動速度が速くなり、切替えに要する時間を短縮することができ、反対に絞り弁４８の開度を小さくすると、絞り弁４８を通る流体の時間当たりの流量が減少してピストン４２の移動速度が遅くなるため、切替えに要する時間を長くすることができる。したがって、シリンダ３０、ピストン４２および絞り弁４８は、圧力調整弁１の設定圧力を低圧から高圧に切り替えるために要する時間を設定する機械的なタイマーを構成することになる。このため、電磁弁や空気式の切換弁などを全く必要とせず、電気や空気圧などの動力がない環境や、停電などの原因で動力が得られなくなった場合でも使用することができる。   The time required for switching from the low pressure setting state to the high pressure setting state can be freely variably set according to the opening of the throttle valve 48. That is, the moving speed of the piston 42 is determined by the opening degree of the throttle valve 48, that is, the flow rate of the fluid passing through the throttle valve 48 per time. Therefore, if the opening degree of the throttle valve 48 is increased, the moving speed of the piston 42 is increased. The time required for switching can be shortened, and conversely, if the opening of the throttle valve 48 is reduced, the flow rate of the fluid passing through the throttle valve 48 is decreased and the moving speed of the piston 42 is decreased. The time required for switching can be lengthened. Therefore, the cylinder 30, the piston 42, and the throttle valve 48 constitute a mechanical timer that sets the time required for switching the set pressure of the pressure regulating valve 1 from the low pressure to the high pressure. For this reason, an electromagnetic valve or a pneumatic switching valve is not required at all, and it can be used even in an environment where there is no power such as electricity or air pressure or when power cannot be obtained due to a power failure or the like.

また、高圧設定時の調節ばね２２のダイアフラム７に対するばね荷重の増加量は、押し棒２５のストッパ５１から上方に突出している突出寸法Ｘ（図１参照）で決定されるため、この突出寸法Ｘを調整することにより、高圧時の設定圧力を微調整することができる。すなわち、ロックナット３６，３７を緩めてシリンダ３０を回転させ、シリンダ３０の高さを変更すると、突出寸法Ｘが微調整されるため、高圧設定時の圧力を微調整することができ、正確な高圧設定を行うことができる。   Further, the amount of increase in the spring load on the diaphragm 7 of the adjustment spring 22 at the time of high pressure setting is determined by the protrusion dimension X (see FIG. 1) protruding upward from the stopper 51 of the push rod 25. By adjusting, the set pressure at the time of high pressure can be finely adjusted. That is, when the lock nuts 36 and 37 are loosened and the cylinder 30 is rotated and the height of the cylinder 30 is changed, the protrusion dimension X is finely adjusted. Therefore, the pressure at the time of setting the high pressure can be finely adjusted. High pressure setting can be made.

このような微調整は、工場での初期設定時に実施される。また、現地に設置後工場集荷時の設定圧力が正しく実現できているかを確認する場合、通水して高圧設定に切り替えた後、二次側の圧力計を見て所望の圧力に対して過不足があった場合、ロックナット３６，３７を緩め、二次側圧力が所望の圧力になるまでシリンダ３０を回転させる。   Such fine adjustment is performed at the time of initial setting in a factory. In addition, when confirming that the set pressure at the time of factory collection has been correctly realized after installation at the site, after switching to high pressure setting by passing water, the pressure on the secondary side can be checked with respect to the desired pressure. If there is a shortage, the lock nuts 36 and 37 are loosened, and the cylinder 30 is rotated until the secondary pressure reaches a desired pressure.

なお、上記した実施の形態では、圧力検出手段としてダイアフラム７を用いた例を示したが、本発明はこれ何ら限定されるものではなく、ピストンやベローズを用いることも可能である。   In the above-described embodiment, an example is shown in which the diaphragm 7 is used as the pressure detecting means, but the present invention is not limited to this, and a piston or a bellows can also be used.

図４は本発明に係る圧力調整弁をパイロット作動式減圧弁に適用し、パイロット弁として用いた例を示す断面図である。
同図において、５３は主弁、５４は弁体、５５はシートリング、５６は弁軸５７を下方に付勢するばね、５８は一次側導管、５９は絞り弁、６１はパイロット弁で、図１に示した圧力調整弁１と同一構造である。流体を通さない状態では、主弁５３はばね５６のばね荷重や弁軸５７の自重により弁体５４が下降してシートリング５５に着座することにより全閉状態に保持されている。 FIG. 4 is a sectional view showing an example in which the pressure regulating valve according to the present invention is applied to a pilot operated pressure reducing valve and used as a pilot valve.
In the figure, 53 is a main valve, 54 is a valve body, 55 is a seat ring, 56 is a spring that urges the valve shaft 57 downward, 58 is a primary side conduit, 59 is a throttle valve, and 61 is a pilot valve. 1 is the same structure as the pressure regulating valve 1 shown in FIG. In a state where fluid is not passed, the main valve 53 is held in a fully closed state by the valve body 54 being lowered and seated on the seat ring 55 by the spring load of the spring 56 and the weight of the valve shaft 57.

この全閉状態より主弁５３の一次側に流体が送られてくると、弁体５４の下面に上向きに作用する一次側流体圧によって弁体５４は上昇してシートリング５５から離間する。このため、流体はシートリング５５と弁体５４との間の流路を通って二次側に流入する。一方、一次側流体は導管５８および絞り弁５９を通って全閉状態のパイロット弁６１に至り、これを通過して二次側に達する。なお、絞り弁５９を通った流体の一部は途中で分岐管６２に分流して主弁５３のダイアフラム室６３に導かれるが、パイロット弁６１が全開しているためダイアフラム室６３内の圧力は上昇せず、主弁５３は開弁状態を維持する。   When fluid is sent to the primary side of the main valve 53 from the fully closed state, the valve body 54 is lifted and separated from the seat ring 55 by the primary fluid pressure acting upward on the lower surface of the valve body 54. For this reason, the fluid flows into the secondary side through the flow path between the seat ring 55 and the valve body 54. On the other hand, the primary side fluid reaches the fully closed pilot valve 61 through the conduit 58 and the throttle valve 59, and passes through this to reach the secondary side. A part of the fluid passing through the throttle valve 59 is diverted to the branch pipe 62 on the way and guided to the diaphragm chamber 63 of the main valve 53. However, since the pilot valve 61 is fully opened, the pressure in the diaphragm chamber 63 is The main valve 53 does not rise and maintains the valve open state.

主弁５３が開弁状態を維持し、二次側に接続された配管に流体の供給を開始すると、徐々に二次側の圧力が上昇するため、パイロット弁６１の二次側圧力も上昇し、ダイアフラム７を上方に変位させる。このため、弁体４は調節ばね２２のばね荷重と釣り合い状態を保つ位置まで閉方向に移動（上昇）する。この結果、パイロット弁６１の二次側圧力は低下し、主弁５３のダイアフラム室６３内の圧力は上昇し、ダイアフラム６４を下方に弾性変形させる。このため、弁体５４は下降してシートリング５５との間の通路を絞り、二次側圧力の上昇を抑える。   When the main valve 53 is kept open and supply of fluid to the pipe connected to the secondary side is started, the pressure on the secondary side gradually increases, so the secondary pressure of the pilot valve 61 also increases. The diaphragm 7 is displaced upward. For this reason, the valve body 4 moves (rises) in the closing direction to a position that maintains a balance with the spring load of the adjustment spring 22. As a result, the secondary pressure of the pilot valve 61 decreases, the pressure in the diaphragm chamber 63 of the main valve 53 increases, and the diaphragm 64 is elastically deformed downward. For this reason, the valve body 54 descends to narrow the passage between the seat ring 55 and suppress the increase of the secondary pressure.

また、二次側圧力の低下により二次側流量が減少すれば、パイロット弁６１のダイアフラム７を下方に動かし、その弁体４を調節ばね２２と釣り合い状態を保つ位置まで開方向に移動させる。この結果、主弁５３のダイアフラム室６３内の圧力は降下し、ダイアフラム６４を上昇させる。このため、弁体５４も上昇してシートリング５５から離間し、シートリング５５との間の流路を広げる。これにより二次側圧力が上昇して流体の不足分が補充される。   Further, if the secondary flow rate decreases due to a decrease in the secondary pressure, the diaphragm 7 of the pilot valve 61 is moved downward, and the valve body 4 is moved in the opening direction to a position that maintains a balanced state with the adjustment spring 22. As a result, the pressure in the diaphragm chamber 63 of the main valve 53 decreases and the diaphragm 64 is raised. For this reason, the valve body 54 is also raised and separated from the seat ring 55, and the flow path between the seat ring 55 is widened. As a result, the secondary pressure rises and the fluid deficiency is replenished.

以上の通り、主弁５３で調整された二次側圧力はパイロット弁６１のダイアフラム７にフィードバックされ、常に調節ばね２２との釣り合い状態を保とうと動作し、主弁５３を動作させるから二次側圧力は一定に保持される。   As described above, the secondary pressure adjusted by the main valve 53 is fed back to the diaphragm 7 of the pilot valve 61, and always operates to maintain a balanced state with the adjustment spring 22, and the main valve 53 is operated. The pressure is kept constant.

以上のパイロット作動式減圧弁の説明は、通水初期の減圧動作の説明であるが、このパイロット弁６１は本発明の設定圧力切替可能な構造であり、圧力設定は低圧設定状態である。そして、通水を開始すると絞り弁４８および導管４５を通過する流体はピストン４２を徐々に押し下げ、これにより絞り弁４８の開度に応じた時間経過後パイロット弁６１の調節ばね２２のばね荷重は自動的に高圧設定に切り替えられるから、パイロット弁６１が開弁して低圧設定の二次側を切り替えられた高圧設定のばね荷重に釣り合う高い二次側圧力まで上昇させる。したがって、このような圧力調整弁６１をパイロット作動式減圧弁に適用すれば、前述したようなウオーターハンマー現象が発生せず、主弁５３の二次側配管が破損するおそれはない。   The above description of the pilot actuated pressure reducing valve is a description of the pressure reducing operation in the initial stage of water flow. The pilot valve 61 has a structure capable of switching the set pressure according to the present invention, and the pressure setting is in the low pressure set state. Then, when the water flow is started, the fluid passing through the throttle valve 48 and the conduit 45 gradually pushes down the piston 42, whereby the spring load of the adjustment spring 22 of the pilot valve 61 is increased after the time corresponding to the opening degree of the throttle valve 48. Since it is automatically switched to the high pressure setting, the pilot valve 61 is opened, and the secondary side of the low pressure setting is raised to a high secondary pressure that is commensurate with the spring load of the switched high pressure setting. Therefore, if such a pressure regulating valve 61 is applied to a pilot operated pressure reducing valve, the water hammer phenomenon as described above does not occur, and there is no possibility that the secondary side piping of the main valve 53 is damaged.

本発明は、設定圧力を二段に切り替える圧力調整弁に適用した例について説明したが、これに限らずその他の弁、例えば背圧弁や差圧弁等の各種自動弁に適用することが可能である。例えば、背圧弁に適用する場合は、一次側の流体圧力をダイアフラム室８と圧力室４３に導き、弁プラグ４Ｂが流体流路６の二次側流路部分に位置するように弁体４を弁本体３内に組み込めばよい。また、差圧弁に適用する場合は、減圧弁と同様に二次側流体圧をダイアフラム室８と圧力室４３に導き、圧力をとる別ラインの圧力をダイアフラムなどの圧力検出手段７の上部に導くようにすればよい。   Although this invention demonstrated the example applied to the pressure control valve which switches setting pressure to two steps, it is not restricted to this, It is possible to apply to various automatic valves, such as a back pressure valve and a differential pressure valve. . For example, when applied to a back pressure valve, the fluid pressure on the primary side is guided to the diaphragm chamber 8 and the pressure chamber 43, and the valve body 4 is placed so that the valve plug 4 </ b> B is positioned in the secondary flow path portion of the fluid flow path 6. What is necessary is just to incorporate in the valve main body 3. When applied to a differential pressure valve, the secondary fluid pressure is led to the diaphragm chamber 8 and the pressure chamber 43 as in the pressure reducing valve, and the pressure of another line for taking pressure is led to the upper portion of the pressure detecting means 7 such as a diaphragm. What should I do?

本発明を高低２種類の圧力設定を可能にした圧力調整弁に適用した一実施の形態を示す断面図で、低圧設定時の状態を示す図である。It is sectional drawing which shows one Embodiment which applied this invention to the pressure regulating valve which enabled two types of high and low pressure setting, and is a figure which shows the state at the time of low pressure setting. 同圧力調整弁を配管に接続した状態を示す断面図で、シリンダーの圧力室に圧力調整弁の二次側圧力を可変型絞り弁を介して導入するようにした接続例を示す図である。It is sectional drawing which shows the state which connected the same pressure regulating valve to piping, and is a figure which shows the example of a connection which introduce | transduced the secondary side pressure of the pressure regulating valve into the pressure chamber of the cylinder via the variable type throttle valve. 同圧力調整弁を高圧設定に切り替えた状態を示す断面図である。It is sectional drawing which shows the state which switched the pressure regulating valve to the high pressure setting. 本発明に係る圧力調整弁をパイロット作動式減圧弁に適用し、パイロット弁として用いた例を示す断面図である。It is sectional drawing which shows the example which applied the pressure regulating valve which concerns on this invention to a pilot actuated pressure reduction valve, and used as a pilot valve.

符号の説明Explanation of symbols

１…圧力調整弁、２…配管、３…弁本体、４…弁体、７…圧力検出手段、８…ダイアフラム室、２２…調節ばね、２５…押し棒、２８…ねじ体、３０…シリンダ、４２…ピストン、４３…圧力室、４４…大気圧室、４５…導管、４８…可変型絞り弁、５０…復帰用ばね、５２…押圧部。
DESCRIPTION OF SYMBOLS 1 ... Pressure control valve, 2 ... Piping, 3 ... Valve body, 4 ... Valve body, 7 ... Pressure detection means, 8 ... Diaphragm chamber, 22 ... Adjustment spring, 25 ... Push rod, 28 ... Screw body, 30 ... Cylinder, 42 ... piston, 43 ... pressure chamber, 44 ... atmospheric pressure chamber, 45 ... conduit, 48 ... variable throttle valve, 50 ... return spring, 52 ... pressing part.

Claims (2)

圧力検出手段の片側に制御対象の流体圧を加え、反対側に圧力設定用の調節ばねのばね荷重を付加することにより前記流体圧を一定に調節する圧力調整弁において、
前記圧力検出手段に前記調節ばねのばね荷重を付加する低圧設定手段と、
前記低圧設定手段を押し下げることにより前記調節ばねのばね荷重を増大させ前記流体圧を低圧から高圧に設定する高圧設定手段と、
前記高圧設定手段の一部が挿入されたシリンダと、
前記シリンダ内を前記高圧設定手段が挿入される大気圧室と圧力室とに仕切り、高圧設定時に前記高圧設定手段を押し下げるピストンと、
前記ピストンに前記圧力室方向の復帰習性を付与する復帰用ばねと、
弁本体への流体供給開始と同時に前記圧力室に高圧設定用の圧力を導く導管と、
前記導管の途中に接続された可変型絞り弁とを備えたことを特徴とする圧力調整弁。 In the pressure regulating valve that adjusts the fluid pressure to a constant level by adding the fluid pressure to be controlled to one side of the pressure detecting means and adding the spring load of the adjusting spring for pressure setting to the opposite side,
Low pressure setting means for adding a spring load of the adjustment spring to the pressure detection means;
High pressure setting means for increasing the spring load of the adjustment spring by pushing down the low pressure setting means and setting the fluid pressure from low pressure to high pressure;
A cylinder into which a part of the high-pressure setting means is inserted;
A piston that divides the inside of the cylinder into an atmospheric pressure chamber and a pressure chamber into which the high-pressure setting means is inserted, and pushes down the high-pressure setting means when setting the high pressure;
A return spring for imparting a return behavior in the pressure chamber direction to the piston;
A conduit for introducing a pressure for setting a high pressure into the pressure chamber simultaneously with the start of fluid supply to the valve body;
A pressure regulating valve comprising a variable throttle valve connected in the middle of the conduit. 請求項１記載の圧力調整弁において、
前記シリンダを前記低圧設定手段に対して高さ調整可能に取付けたことを特徴とする圧力調整弁。
The pressure regulating valve according to claim 1,
A pressure regulating valve, wherein the cylinder is attached to the low pressure setting means so as to be adjustable in height.
JP2003320247A 2003-09-11 2003-09-11 Pressure regulating valve Expired - Fee Related JP4282415B2 (en)

Priority Applications (1)

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JP2003320247A JP4282415B2 (en) 2003-09-11 2003-09-11 Pressure regulating valve

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CN100398890C (en) * 2006-04-17 2008-07-02 清华大学 Powerless mechanical feedback type automatic adjustment valve of air-feed flow
JP5331180B2 (en) * 2011-09-22 2013-10-30 株式会社フジキン Valve stroke adjustment method for direct touch type metal diaphragm valve
JP2014106700A (en) * 2012-11-27 2014-06-09 Azbil Kimmon Co Ltd Direct-acting regulator
JP2014191529A (en) * 2013-03-27 2014-10-06 Keihin Corp Pressure reduction valve
JP5833722B1 (en) * 2014-09-01 2015-12-16 フシマン株式会社 Self-regulating regulator
CN104879543A (en) * 2015-06-08 2015-09-02 德阳正光机电设备有限公司 Automatic-control constant-pressure throttling valve

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